EP2130105A2

EP2130105A2 - Pressure valve

Info

Publication number: EP2130105A2
Application number: EP08734671A
Authority: EP
Inventors: Georg Schoppel; Daniel Barriga
Original assignee: Robert Bosch GmbH
Current assignee: Robert Bosch GmbH
Priority date: 2007-03-20
Filing date: 2008-03-19
Publication date: 2009-12-09
Anticipated expiration: 2028-03-19
Also published as: WO2008113572A2; US20100090136A1; DE502008000843D1; CN101652735A; WO2008113572A3; CN101652735B; EP2130105B1; DE102007013152A1; ATE472126T1

Abstract

A pressure valve comprises a valve bush and a control plunger which is movably guided in the valve bush and enables a pressure medium path from a pressure medium source to a consumer via the valve bush to be controlled. A collar section is provided on the control plunger, via which the cross section of a radial opening of the valve bush on the side of the pressure medium source may be modified. The pressure medium path downstream of the radial opening is guided by at least one channel which extends axially through the collar section. The pressure valve also comprises a pilot control system which is used to apply an adjustable control pressure to the control plunger; a control pressure medium supply channel comprising an inlet opening is provided on the control plunger in a region upstream of the collar section. The invention is characterized by the fact that the at least one axially extending channel is dimensioned in such a way that pressure medium may accumulate on the collar section.

Description

pressure valve

description

The invention relates to a pressure valve according to the preamble of patent claim 1.

Pressure valves, in particular pilot operated 2-way or 3-way pressure reducing valves, are used in hydraulic control technology when a pressure at a consumer connection according to a specification should be kept as constant as possible. Areas of application are e.g. hydraulic presses, clamping devices on machine tools, etc. In contrast to the requirement to keep a pressure constant at almost any flow rates, real pressure reducing valves usually have a falling control characteristic, i. as the flow rate increases, the control pressure drops - with the pressure set constant. This behavior is attributed to the flow forces, which act on the control piston with increasing flow rate in the closing direction.

In the case of housing valves, the characteristic curve could be improved and the valve could also be simplified in terms of construction by tapping off control pressure fluid from a cavity in the control piston of the valve. In this cavity already prevails the regulated

Print. By tapping off control pressure means on the end face of the cavity, a favorable control pressure medium characteristic curve is achieved and a closing of the control piston at high flow rates is prevented. This valve construction is disclosed in DE 196 15 789 A1.

In the case of pressure valves, attempts are still made to design as cost-effectively as possible and to reduce the variety of types by means of a wide range of applications. Therefore, in particular pressure reducing valves are increasingly designed as Einschraubventile both for stationary hydraulics and for mobile hydraulics. Such a generic pressure valve is e.g. in the data sheet RD 18111-02 / 06.05 of the company

Bosch Rexroth AG.

The present invention is directed to specifying an improved with respect to its control pressure characteristic pressure valve in Einschraubventiltechnik. This object is achieved by a pressure valve having the features of patent claim 1.

According to the invention, a pressure valve is provided with a valve bushing and with a control piston movably guided in the valve bush, by means of which a pressure medium path provided via the valve bushing from a pressure medium source to a consumer is controllable. On the control piston, a collar portion is provided, through which an opening cross-section at a pressure medium-source-side radial opening of the valve sleeve is variable. The Druckmittelweg downstream of the radial opening is guided by at least one axially extending through the collar portion channel. Furthermore, one of the loading of the control piston with an adjustable

Pilot pressure serving pilot control arrangement is provided, wherein a control pressure medium supply channel is provided with an inlet opening on the control piston in an area upstream of the collar portion.

The peculiarity is that the at least one axially extending channel is dimensioned so that pressure medium on the collar portion is anstaubar. In this way, the input pressure at the control pressure medium supply passage can be increased depending on an increasing flow rate. Consequently, the control pressure acting on the control piston in the control pressure chamber can be influenced in the sense of a linearization of the pressure medium quantity - control pressure - characteristic. Also noteworthy is the particularly simple design of the valve. Compared to conventional valves, the control piston is modified in particular. This can be represented as a simple cylindrical body or as a stepped piston. Thus, a simple cost-efficient manufacturability of a pressure valve according to the present invention - while ensuring excellent uniform pressure behavior - guaranteed.

Advantageous embodiments of the present invention are specified in the subclaims.

According to a preferred embodiment of the control piston is designed as a stepped piston, which continues axially, starting from the first, aforementioned collar portion in a radially recessed neck portion and then into a second collar portion. Such a control piston is easy to manufacture and allows the production of the required channels through simple holes. Preferably, the control piston is guided at both collar portions in the valve sleeve, whereby a good seal and a reliable function is achieved.

According to a particularly preferred embodiment of the present invention, the control pressure medium supply channel of an axially oriented surface of the second collar portion or of a portion of the neck portion, in particular the

Lateral surface, near the second collar section. This ensures reliable supply of the pilot control arrangement with control pressure means from a region in which uniform pressure conditions prevail.

The range of application of the pressure valve according to the invention is wider, if this than

3-way valve is executed, wherein according to an advantageous design, the second collar portion controls an opening cross-section of a connected to a discharge line radial opening of the valve sleeve.

A particularly preferred embodiment provides that a second control pressure medium supply channel is provided, which has an inlet opening on a side of the first collar portion facing away from the neck portion. This ensures a reliable supply to the pilot control arrangement with control pressure means even in a pressure limiting operation in which pressure medium is discharged from the consumer connection to the tank.

Preferably, a check valve is arranged in the second control pressure medium supply channel, which allows according to its passage direction an inflow of pressure medium at the inlet opening of the second control pressure medium supply channel. In the pressure reducing operation, in which pressure medium is supplied to the load from the pressure medium source, the check valve prevents, due to the pressure conditions, an inflow of control pressure medium into the second control pressure medium supply channel. In this case, the control pressure medium supply only takes place through the first control pressure medium supply channel, so that the desired dependence of the control pressure medium supply quantity on the flow rate passed through the valve is maintained.

The two control pressure medium supply channels are particularly easy to manufacture when the second control pressure medium supply channel in the first control pressure medium supply channel opens. Preferably, a bore axially passing through the control piston is provided in sections for forming the first control pressure medium supply channel and the second control pressure medium supply channel. It is furthermore advantageous if the inlet opening of the first control-pressure-medium supply channel is formed by a radial bore opening into the axial bore.

According to a particularly preferred embodiment, a plurality of continuous axial bores are provided circumferentially in the collar section, which open in a ring section of the collar section facing the neck section. In this design, the total cross section of the channels through the first collar section can be set very accurately. Furthermore, a large inflow chamber for the pressure medium inlet can be formed on the neck section via the radial opening of the valve bushing. This makes it possible to arrange the opening of the control-pressure-medium supply passage at a sufficient distance from the control edge at the first collar portion. The removal of control pressure medium takes place from a flow-calmed area. The pressure ratios at the opening of the control pressure medium supply channel are in particular independent of the angular position of the control piston.

Particularly constructive and simple to manufacture in manufacturing is the pressure valve, if in the neck portion a continuous radial bore is executed, and if in the first collar portion opening into the said radial bore

Axial bore is provided. The diameter of the axial bore according to the invention is chosen to be smaller than the diameter of the radial bore.

According to a particularly preferred embodiment, the pilot control arrangement causes a rise in the case of an increase in the amount of control fluid supplied to it

Control pressure. In this way, the flow forces acting in the closing direction can be directly compensated. Preferably, the pilot control arrangement is equipped with a directly operated pressure relief valve. Such a pressure relief valve is inexpensive and has the desired characteristic.

Hereinafter, the present invention and its advantages will be explained in more detail with reference to the embodiments illustrated in the figures. Figure 1 is a cross-sectional view of a pressure valve with a stepped one

Control piston and annularly arranged axial bores in the consumer connection side collar portion of the control piston,

FIG. 2 shows a variant of a pressure valve corresponding to FIG. 1, in which the control piston has an additional control pressure medium inlet opening in the end face on the consumer connection side,

Figure 3 is a cross-sectional view of a pressure valve according to another embodiment of the invention, in which the control piston has a Druckmittelweg arranged in the radial bore and an axial bore, and

FIG. 4 is a cross-sectional view, rotated by 90 °, of the pressure valve shown in FIG.

According to Figure 1, a 3-way pressure reducing valve 1 is designed as a screw-3, which is intended for installation in a mounting hole 4 of a valve block 5. The valve block 5 has connecting bores opening into the installation bore 4, which are assigned to a pressure medium source connection P, a tank connection T and a consumer connection A of the valve 1. The screw-in valve 3 comprises, as usual, a fastening sleeve 7 and a valve sleeve 9 held in the fastening sleeve 7 in which a control piston 11 is movably guided.

In the mounting sleeve 7, a pilot valve is arranged. The pilot valve is designed as a pressure relief valve 12 in the valve seat design. By one with a

Damper nozzle provided seat sleeve 14 is the fluidic connection to a

Control pressure chamber 15 given. A control cone 16 is acted upon by a compression spring 18 with a force in the direction of the seat sleeve 14. The opening pressure of the

Pressure relief valve 12 can be adjusted via the force acting on the compression spring 18 adjustment sleeve 20.

The valve bushing 9 has a first ring of radial bores 22, which are arranged in a pressure medium supply region 21 of the mounting hole 4, and a second ring of radial bores 24, which in a tank connection region 23 of the Mounting hole 4 are arranged. The frontal opening 25 of the valve sleeve is fluidly connected to the consumer port A. The guided in the valve sleeve 9 control piston 1 1 is in a first collar portion 27 which faces the opening 25, a neck portion 29 and a second collar portion 31 which limits the control pressure chamber 15, axially divided. The first collar portion 27 has a ring on axially extending holes 33, which in a neck portion 29 facing

Open ring surface 34. The second collar portion 31 is provided on its the control pressure chamber 15 side facing with a recess. At the bottom of the recess, an axial bore 36 is designed as a blind hole. Together with a radially into the neck portion 29 in the immediate vicinity of the second collar portion 31 introduced nozzle bore 37, the axial bore 36 forms a control pressure medium supply channel for the control pressure chamber 15. In the control pressure chamber 15, a compression spring 39 is received at the bottom of the recess of the second collar portion 31 and supported on an annular surface of the fastening sleeve 7. This compression spring 39 acts on the control piston with a directed in the direction of the opening 25 force.

The function of the pressure reducing valve 1 shown in FIG. 1 will be explained below. The pressure set in the consumer port A is determined by a force equilibrium condition on the control piston 11. At a pressure medium flow from P to A, the control piston 1 1 assumes a position in which a balance of in the sense of closing the radial bores 22 and in the

The sense of opening the radial bores 22 acting forces prevails. These are the hydrostatic forces acting on the consumer connection A on the one hand and the force caused by the control pressure in the control pressure chamber 15 and the force of the compression spring 39 on the other hand. Thus, the control piston 1 1 controls the pressure in the consumer port A according to the specification of the control pressure and the force of the compression spring

39, which is usually chosen low. In the case of a pressure medium flow from A to T, the equilibrium of forces just described also applies. The control piston 11 assumes a position in which it controls an outflow of pressure medium at the radial bores 24. In this pressure medium flow direction, the pressure in the load port A is corresponding to the control pressure and the force of the compression spring

39 limited.

In the direction of flow of the pressure medium from P to A results from the restriction of the flow cross section at the axial bores 33, a pressure drop across the first collar portion 27. The pressure medium is accumulated upstream of the first collar portion 27 so to speak. The increase of the pressure on the neck side of the control piston

11 with respect to the consumer port A is the higher, the greater the flowing pressure medium quantity. A higher pressure at the neck portion 29 of the control piston 11 causes an increase of the flowing through the nozzle bore 37 in the control pressure chamber 15 control pressure medium amount. Due to the increasing amount of control fluid - control pressure - characteristic of the pressure relief valve

12, the control pressure in the control pressure chamber 15 increases with the pressure medium flowing through the path P to A. The increased control pressure amplifies the force acting on the control piston 11 in the sense of opening the radial bores 22. This acts to reinforce the pressure medium acting in the closing direction Contrary to flow forces. In this way, a nearly constant pressure medium quantity - control pressure - characteristic of the pressure reducing valve 1 can be achieved.

With knowledge of the described invention, the skilled person will determine the required

Cross section of the axial bores 33 and the required increase in the control pressure medium quantity - control pressure - characteristic of the pressure relief valve 12 by in the usual calculations or experiments.

Of course, the invention is also readily applicable to 2-way pressure reducing valves. Such a 2-way pressure reducing valve can be easily specified by dispensing with the tank connection and the associated radial bores 24. The described compensation of the flow forces in the flow direction P to A remains unaffected.

A variant of the pressure reducing valve 1 shown in Figure 1 is shown in Figure 2 with reference to the 3-way pressure reducing valve 2. Its structure largely corresponds to the structure of the pressure reducing valve 1. Differences exist only in the control pressure medium supply. The same reference signs are used for the same features. In the following description of the pressure reducing valve 2, only the said differences to the pressure reducing valve 1 are indicated.

In contrast to the axial bore 36 designed as a blind bore, the control piston 11 of the pressure reducing valve 2 has a control piston 11 on its entire length continuous stepped axial bore 41 available. In the axial bore 41 opens in the immediate vicinity of the shoulder of the second collar portion 31, the nozzle bore 37. Further in the direction of the opening 25 of the valve sleeve 9 facing end face 35 of the control piston 11 in the stepped axial bore 41 successively a nozzle insert 43, a check valve 45 and the mouth opening of the axial bore 41 an inlet attachment piece 47 is arranged.

In the pressure reducing operation, in a flow direction of the pressure medium from P to A, the pressure in the region of the neck portion 29 due to the constriction of the pressure medium path through the axial bores 33 is slightly higher than the pressure at the consumer port A, i. as at the inlet attachment piece 47. The check valve 45 therefore remains closed. A supply of control pressure medium in the control pressure chamber 15 takes place only via the nozzle bore 37. An outflow of control pressure medium in the direction of the end face 35 is prevented by the check valve 45. The desired increase in the amount of control fluid is obtained with the amount of pressure medium conducted via the valve.

In the pressure limiting operation, in a flow direction of the pressure medium A to T, however, the pressure at the inlet attachment piece 47 is higher than the pressure at the nozzle bore 37. The check valve 45, which has a very weak spring, opens and allows the flow of control fluid into the control pressure chamber 15 from the area in front of the end face 35 of the control piston 11. At a high pressure gradient across the first collar portion 27 would be alone from the nozzle bore 37 no sufficient control pressure supply more possible, causing a deterioration of the pressure limiting function or at worst a demolition of the control oil supply and a sudden Break away the pressure held at port A could be done. Due to the influx of control pressure medium from the area in front of the end face 35, to which, as stated, an increased pressure accumulates, the reliable control pressure medium supply is ensured. The control pressure medium quantity supplied via the inlet attachment piece 47 can be defined via the inner diameter of the nozzle insert 43.

Another embodiment of the present invention is illustrated in FIGS. 3 and 4 with reference to a 3-way pressure reducing valve 50. The illustration in FIG. 4 is rotated by 90 ° with respect to the illustration in FIG. 3 about the valve axis. The Pressure reducing valve 50 is designed as Einschraubventil as in the first embodiment. The 3-way pressure reducing valve 50 differs only by the design of the control piston 1 1 of the pressure reducing valve 2 described above. The same reference numerals are used for the same features. In the following description of the pressure reducing valve 50, the said differences to the pressure reducing valve 2 are mainly indicated.

The control piston 11 is in turn provided as a stepped piston with a first of the valve sleeve opening 25 facing first collar portion 27, a neck portion 29 and a control pressure chamber 15 facing the second collar portion 31. The pressure in the control pressure chamber 15 is not shown by a

Pilot valve, preferably set a arranged in the mounting sleeve 7 pressure relief valve.

In contrast to the pressure reducing valve 1 or 2, the neck portion 29 of the control piston 11 of the pressure reducing valve 50 springs back radially only slightly so that it can also be regarded as a circumferential groove in the lateral surface of the control piston 11. The neck portion 29 is penetrated by a radial bore 54 whose diameter corresponds to almost the width of the neck portion 29. Instead of a ring of axially running holes 33, only a centrally disposed axial bore 52 is present, which emanates from the end face 35, starting in the radial bore 54. The diameter of the axial bore 52 is smaller than the diameter of the radial bore 54. Another, stepped axial bore forms the control pressure medium supply channel 56 in the second collar portion 31. The radial bore 54 facing the end portion of the control pressure medium supply channel 56 is designed as a nozzle bore.

As shown in Figure 4, an additional, executed in the jacket of the control piston 11 control pressure medium supply channel 60 is present. This is provided with a nozzle insert 43 and with a check valve 62, which at an appropriate pressure conditions an inflow of control pressure medium in the

Control pressure chamber 15 allows from the front side 35 ago. The control pressure medium supply channel 60 is preferably designed as a stepped axial bore. The function of the pressure reducing valve 50 corresponds to the function of the pressure reducing valve 2. In a pressure medium flow direction from P to A - in Druckreduzierbetrieb - created by the narrowing of the cross section of the axial bore 52, a pressure drop across the first collar section 27. Pressure medium is thereby upstream of the first collar section 27 in Area of the neck portion 29 accumulated in a sense. The pressure gradient increases with increasing amount of pressure medium. As the amount of pressure medium increases, the pressure at the inlet opening of the control pressure medium supply channel 56 and thus the supplied control pressure medium quantity increases. This allows the already described compensation of the forces acting on the control piston 11 flow forces and thus a nearly constant pressure medium quantity - control pressure - characteristic of the pressure reducing valve on the rising control pressure characteristic

50. In this pressure medium flow direction, the check valve 62 remains closed.

In a pressure medium flow direction from A to T - in the pressure limiting operation - allows the additional provided with the check valve 62 Steuerdruckmittel- supply channel 60 a secure supply of the control pressure chamber 15 with

Control fluid. This applies in particular to high pressure medium flows A to T, in which due to the pressure gradient forming over the first collar section 27, a secure pressure medium supply alone via the control pressure medium supply channel 56 would not be possible.

Combinations of features of the first embodiment with features of the second embodiment are intended to be encompassed by the invention. Thus, the pressure reducing valve 50 can be easily formed as a 2-way pressure reducing valve by dispensing with the radial bores 24. Then, the additional control pressure medium supply channel 60 with the check valve 62 and the nozzle insert 43 - comparable to the embodiment of Figure 1 - dispensable. Also, a 3-way pressure reducing valve 50 can be limited without the additional control pressure medium supply channel 60, without the check valve 62 and without the restriction of the maximum volume to be dissipated to the tank or with only a slight narrowing of the flow path through the axial bore 52

Nozzle insert 43 are executed. LIST OF REFERENCES

1 pressure reducing valve

2 pressure reducing valve

3 screw-in valve

4 installation hole

5 valve block

7 mounting sleeve

9 valve socket

11 control piston

12 pressure relief valve

14 seat sleeve

15 control pressure chamber

16 tax cones

18 compression spring

20 adjusting sleeve

21 pressure medium supply area

22 radial bores

23 tank connection area

24 radial bores

25 opening

27 first fret section

29 neck section

31 second collar section

33 axial bores

34 ring surface

35 front side

36 axial bore

37 nozzle bore

39 compression spring

41 axial bore

43 nozzle insert

45 check valve

47 inlet attachment

50 pressure reducing valve

52 axial bore 54 radial bore

56 Control pressure medium supply channel with nozzle bore

60 control pressure medium supply channel

62 check valve

A Consumer connection P Pressure medium source connection

T tank connection

Claims

claims

1. pressure valve with a valve bushing (9) and with a in the valve sleeve (9) movably guided control piston (11) through which via the valve sleeve (9) provided by a pressure medium source to a consumer Druckmittelweg is controllable, wherein the control piston (11 ) a collar portion (27) is provided, through which an opening cross section at a pressure medium source side radial opening (22) of the valve sleeve (9) is variable, and wherein the Druckmittelweg downstream of the radial opening (22) by at least one axially through the collar portion (27) extending A control pressure medium supply channel (36, 37, 56) with an inlet opening on the control piston (1 1) in a Region upstream of the collar portion (27) is provided, characterized in that the at least one axially extending channel (33; 52) is dimensioned so that pressure medium on the collar portion (27) is anstaubar.

2. Pressure valve according to claim 1, characterized in that the control piston

(11) is formed as a stepped piston and continues axially from the first, aforementioned collar portion (27) in a radially recessed neck portion (29) and then in a second collar portion (31).

3. Pressure valve according to claim 2, characterized in that the control piston

(11) at both collar portions (27, 31) in the valve sleeve (9) is guided.

4. Pressure valve according to claim 2 or 3, characterized in that the control pressure medium supply channel (36, 37, 56) of an axially oriented surface of the second collar portion (31) or of a region of the neck portion (29), in particular the lateral surface, near the second Bundabschnitts (31) goes out.

5. Pressure valve according to one of claims 2 to 4, characterized in that the second collar portion (31) has an opening cross-section at one with a Ent- load line fluidly connected radial opening (24) of the valve sleeve (9) controls.

6. Pressure valve according to claim 5, characterized in that a second control pressure medium supply channel (41; 60) is provided, which has an inlet opening on a side facing away from the neck portion (29) (35) of the first collar portion

(27).

7. A pressure valve according to claim 6, characterized in that in the second control pressure medium supply channel (41; 60) a check valve (45; 62) is arranged, which allows according to its passage direction an inflow of pressure medium at the inlet opening of the second control pressure medium supply channel (41; 60).

8. A pressure valve according to claim 7, characterized in that the second control pressure medium supply channel in the first control pressure medium supply channel Mün- det.

9. Pressure valve according to claim 8, characterized in that the control piston (11) axially continuous bore (41) is provided in sections for forming the first control pressure medium supply channel and the second Steuerdruckmittelzufuhr- channel.

10. Pressure valve according to claim 9, characterized in that the inlet opening of the first control pressure medium supply channel is formed by an opening into the axial bore (41) radial bore (37).

11. Pressure valve according to one of claims 1 to 10, characterized in that in the collar portion (27) circumferentially more continuous axial bores (33) are provided, which in a neck portion (29) facing annular surface (34) of the collar portion (27) open ,

12. Pressure valve according to one of claims 2 to 10, characterized in that in the neck portion (29) has a continuous radial bore (54) is designed that in the first collar portion (27) into said radial bore (54) opening out axial bore (52 ), and that the diameter of the axial bore (52) is less than the diameter of the radial bore (54).

13. Pressure valve according to one of the preceding claims, characterized in that the pilot control arrangement (12) causes an increasing control pressure with an increase in the control pressure medium supplied to it.

14. Pressure valve according to one of the preceding claims, characterized in that the pilot control arrangement comprises a directly operated pressure relief valve (12).